US5734530A - Head drum assembly incorporating therein parts coated with diamond-like carbon - Google Patents

Head drum assembly incorporating therein parts coated with diamond-like carbon Download PDF

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Publication number
US5734530A
US5734530A US08/573,832 US57383295A US5734530A US 5734530 A US5734530 A US 5734530A US 57383295 A US57383295 A US 57383295A US 5734530 A US5734530 A US 5734530A
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US
United States
Prior art keywords
rotating shaft
drum
stationary
rotary drum
dlc
Prior art date
Legal status (The legal status is an assumption and is not a legal conclusion. Google has not performed a legal analysis and makes no representation as to the accuracy of the status listed.)
Expired - Fee Related
Application number
US08/573,832
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English (en)
Inventor
Keum-Mo Kim
Current Assignee (The listed assignees may be inaccurate. Google has not performed a legal analysis and makes no representation or warranty as to the accuracy of the list.)
WiniaDaewoo Co Ltd
Original Assignee
Daewoo Electronics Co Ltd
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Filing date
Publication date
Priority claimed from KR1019940037247A external-priority patent/KR100213272B1/ko
Priority claimed from KR2019940036239U external-priority patent/KR960024772U/ko
Application filed by Daewoo Electronics Co Ltd filed Critical Daewoo Electronics Co Ltd
Assigned to DAEWOO ELECTRONICS, CO., LTD. reassignment DAEWOO ELECTRONICS, CO., LTD. ASSIGNMENT OF ASSIGNORS INTEREST (SEE DOCUMENT FOR DETAILS). Assignors: KIM, KEUM-MO
Application granted granted Critical
Publication of US5734530A publication Critical patent/US5734530A/en
Assigned to DAEWOO ELECTRONICS CORPORATION reassignment DAEWOO ELECTRONICS CORPORATION ASSIGNMENT OF ASSIGNORS INTEREST (SEE DOCUMENT FOR DETAILS). Assignors: DAEWOO ELECTRONICS CO., LTD.
Anticipated expiration legal-status Critical
Expired - Fee Related legal-status Critical Current

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Classifications

    • F—MECHANICAL ENGINEERING; LIGHTING; HEATING; WEAPONS; BLASTING
    • F16—ENGINEERING ELEMENTS AND UNITS; GENERAL MEASURES FOR PRODUCING AND MAINTAINING EFFECTIVE FUNCTIONING OF MACHINES OR INSTALLATIONS; THERMAL INSULATION IN GENERAL
    • F16C—SHAFTS; FLEXIBLE SHAFTS; ELEMENTS OR CRANKSHAFT MECHANISMS; ROTARY BODIES OTHER THAN GEARING ELEMENTS; BEARINGS
    • F16C33/00—Parts of bearings; Special methods for making bearings or parts thereof
    • F16C33/02—Parts of sliding-contact bearings
    • F16C33/04—Brasses; Bushes; Linings
    • F16C33/06—Sliding surface mainly made of metal
    • F16C33/10—Construction relative to lubrication
    • F16C33/1025—Construction relative to lubrication with liquid, e.g. oil, as lubricant
    • F16C33/106—Details of distribution or circulation inside the bearings, e.g. details of the bearing surfaces to affect flow or pressure of the liquid
    • F16C33/107—Grooves for generating pressure
    • F—MECHANICAL ENGINEERING; LIGHTING; HEATING; WEAPONS; BLASTING
    • F16—ENGINEERING ELEMENTS AND UNITS; GENERAL MEASURES FOR PRODUCING AND MAINTAINING EFFECTIVE FUNCTIONING OF MACHINES OR INSTALLATIONS; THERMAL INSULATION IN GENERAL
    • F16C—SHAFTS; FLEXIBLE SHAFTS; ELEMENTS OR CRANKSHAFT MECHANISMS; ROTARY BODIES OTHER THAN GEARING ELEMENTS; BEARINGS
    • F16C17/00—Sliding-contact bearings for exclusively rotary movement
    • F16C17/02—Sliding-contact bearings for exclusively rotary movement for radial load only
    • F16C17/026—Sliding-contact bearings for exclusively rotary movement for radial load only with helical grooves in the bearing surface to generate hydrodynamic pressure, e.g. herringbone grooves
    • F—MECHANICAL ENGINEERING; LIGHTING; HEATING; WEAPONS; BLASTING
    • F16—ENGINEERING ELEMENTS AND UNITS; GENERAL MEASURES FOR PRODUCING AND MAINTAINING EFFECTIVE FUNCTIONING OF MACHINES OR INSTALLATIONS; THERMAL INSULATION IN GENERAL
    • F16C—SHAFTS; FLEXIBLE SHAFTS; ELEMENTS OR CRANKSHAFT MECHANISMS; ROTARY BODIES OTHER THAN GEARING ELEMENTS; BEARINGS
    • F16C17/00—Sliding-contact bearings for exclusively rotary movement
    • F16C17/10—Sliding-contact bearings for exclusively rotary movement for both radial and axial load
    • F16C17/102—Sliding-contact bearings for exclusively rotary movement for both radial and axial load with grooves in the bearing surface to generate hydrodynamic pressure
    • F16C17/107—Sliding-contact bearings for exclusively rotary movement for both radial and axial load with grooves in the bearing surface to generate hydrodynamic pressure with at least one surface for radial load and at least one surface for axial load
    • G—PHYSICS
    • G11—INFORMATION STORAGE
    • G11B—INFORMATION STORAGE BASED ON RELATIVE MOVEMENT BETWEEN RECORD CARRIER AND TRANSDUCER
    • G11B5/00—Recording by magnetisation or demagnetisation of a record carrier; Reproducing by magnetic means; Record carriers therefor
    • G11B5/48—Disposition or mounting of heads or head supports relative to record carriers ; arrangements of heads, e.g. for scanning the record carrier to increase the relative speed
    • G11B5/52—Disposition or mounting of heads or head supports relative to record carriers ; arrangements of heads, e.g. for scanning the record carrier to increase the relative speed with simultaneous movement of head and record carrier, e.g. rotation of head
    • G11B5/53—Disposition or mounting of heads on rotating support
    • F—MECHANICAL ENGINEERING; LIGHTING; HEATING; WEAPONS; BLASTING
    • F16—ENGINEERING ELEMENTS AND UNITS; GENERAL MEASURES FOR PRODUCING AND MAINTAINING EFFECTIVE FUNCTIONING OF MACHINES OR INSTALLATIONS; THERMAL INSULATION IN GENERAL
    • F16C—SHAFTS; FLEXIBLE SHAFTS; ELEMENTS OR CRANKSHAFT MECHANISMS; ROTARY BODIES OTHER THAN GEARING ELEMENTS; BEARINGS
    • F16C2370/00—Apparatus relating to physics, e.g. instruments
    • F16C2370/12—Hard disk drives or the like

Definitions

  • the present invention relates to a head drum assembly for use in a video cassette recorder ("VCR"); and, more particularly, to a head drum assembly capable of providing an improved rotatability in a rotary drum incorporated therein.
  • VCR video cassette recorder
  • a head drum assembly for use in a VCR comprises a plurality of moving parts, e.g., a rotary drum, and stationary parts, e.g., a stationary drum.
  • moving parts e.g., a rotary drum
  • stationary parts e.g., a stationary drum.
  • the head drum assembly is broadly classified as either a ball bearing type or a sliding bearing type, depending on how the moving parts and the stationary parts are mechanically interrelated.
  • FIG. 1 a conventional ball bearing type head drum assembly comprising: a rotating shaft 1 divided into an upper part 1a, a middle part 1b, and a motor attachment part 1c; a rotary drum 2 provided with a protruding annular portion on its bottom surface and a plurality of heads (not shown), and fitted tightly around the upper part 1a of the rotating shaft 1; two sets of ball bearings 5 arranged around the middle part 1b of the rotating shaft 1; a stationary drum 4 fitted around the two sets of ball bearings 5; a motor assembly 3 tightly fitted around the motor attachment part 1c of the rotating shaft 1; a rotor transformer 6 attached to the protruding annular portion on the bottom surface of the rotary drum 2; a stator transformer 7 installed on the stationary drum 4 and facing the rotor transformer 6 while maintaining a set distance therefrom; a thrust support bowl 8 attached to a bottom surface of a rim (not shown) of the stationary drum 4 and filled with a lubricant 9; and a thrust support knob 8a provided
  • the thrust support bowl 8 and the thrust support knob 8a provided at the center thereof serve to maintain a predetermined separation between the rotary drum 2 and the stationary drum 4. Since the thrust support bowl 8 is fixed to the stationary drum 4, the thrust support knob 8a attached to the center of the thrust support bowl 8 prevents the rotating shaft 1 and the rotary drum 2 from moving too far down axially in relation to the stationary drum 4. This, in turn, prevents an occurrence of friction due to a direct contact between the rotary drum 2 and the stationary drum 4. To further facilitate an easy rotation of the rotating shaft 1 and the rotary drum 2, the thrust support knob 8a is made of a material with a low friction coefficient, e.g. a polished ruby, thus reducing its friction with the rotating shaft 1. In addition, the thrust support bowl 8 is filled up to a tip (not shown) of the thrust support knob 8a with the lubricant 9. The lubricant 9 reduces the friction between the rotating shaft 1 and the thrust support knob 8a even further.
  • the ball bearings 5 arranged around the rotating shaft 1 serve to facilitate the rotation of the rotating shaft 1 and the rotary drum 2 in relation to the stationary drum 4. Since the stationary drum 4 and the rotating shaft 1 interact with each other only through the ball bearings 5 which are capable of rolling easily, the rotating shaft 1 can rotate in relation to the stationary drum 4 with a minimum of friction.
  • this design permits the rotating shaft 1 and the rotary drum 2 to rotate as intended, an irregularity in any one of the ball bearings 5 may give rise to vibrations and cause the rotary drum 2 to rotate in an irregular manner, affecting the ability of the heads attached thereto to read data stored on a magnetic tape, which will in turn adversely affect the performance of the VCR.
  • this design demands a high level of precision during a manufacturing process thereof: if the two sets of ball bearings 5 are not aligned perfectly together, it is virtually impossible to insert the rotating shaft 1 therethrough.
  • the lubricant 9 held in the thrust support bowl 8 may contaminate the heads, leading to a deterioration of image quality. Also, the lubricant 9 that has to be poured into the thrust support bowl 8 must be carefully measured, lowering the production efficiency of the head drum assembly.
  • FIG. 2 illustrates a conventional sliding bearing type head drum assembly, comprising: a stationary shaft 10 provided with an upper portion 10a and a lower portion 10b, and a plurality of herring-bone shaped grooves or protrusions formed on the upper portion 10a thereof, thereby giving rise to a first set of bearing surfaces 11; a rotary drum 40 fitted around the upper portion 10a of the stationary shaft 10, and equipped with a second set of bearing surfaces 31 that match the first set of bearing surfaces 11; and a stationary drum 20 that fits tightly around the lower portion 10b of the stationary shaft 10.
  • a thrust bearing 50 with herring-bone shaped grooves on its bottom surface 51, is attached to the rotary drum 40 and serves to constrain the rotary drum 40 from moving towards and coming in contact with the stationary drum 20.
  • the rotary drum 40 and the stationary shaft 10 are in contact only through their respective bearing surfaces 31 and 11, allowing the rotary drum 40 to rotate easily around the stationary shaft 10.
  • the rotatability of the rotary drum 40 is further enhanced by applying a lubricant between the first set of bearing surfaces 11 of the stationary shaft 10 and the second set of bearing surfaces 31.
  • the lubricant applied between the bearing surfaces 11 and 31 reduces friction between the rotary drum 40 and the stationary shaft 10.
  • the lubricant lowers both a static friction coefficient and a dynamic friction coefficient during rotation between the stationary shaft 10 and the rotary drum 40.
  • the lubricant allows easy rotation of the rotary drum 40 and also keeps the bearing surfaces 11 and 31 from abrading away when the rotary drum 40 is just beginning to rotate.
  • the herring-bone shaped grooves or protrusions serve to continuously draw in the lubricant into a space between the bearing surfaces 11 and 31 and thus further facilitate the rotation of the rotary drum 40.
  • the sliding bearing type head drum assembly is likely to provide more stable rotation of the rotary drum 40 in comparison with the ball bearing type head drum assembly, since the former does not make use of ball bearings, eliminating the instability problem of the rotary drum 40 due to vibrations caused by irregularities in the ball bearings.
  • the lubricant 9 used in the ball bearing type head drum assembly described above may contaminate the heads, thus adversely affecting the performance of the VCR.
  • the amount of lubricant that has to be injected and applied between the bearing surfaces has to be carefully measured, thus lowering the production efficiency.
  • the production efficiency is further lowered due to the fact that it is very difficult to form the herring-bone shaped grooves or protrusions on the bearing surfaces 11.
  • a head drum assembly for use in a VCR comprising: a rotating shaft provided with a circumferential surface and divided into an upper part and a lower part; a rotary drum, fitted tightly around the upper part of the rotating shaft and furnished with a protruding annular portion on its bottom surface; a rotor transformer attached to the protruding annular portion of the rotary drum; a stationary drum rotatably fitted around the lower part of the rotating shaft and provided with a top surface and an annular depression therein; a stator transformer attached to a bottom surface of the annular depression on the top surface of the stationary drum; a DLC coating applied on the circumferential surface of the rotating shaft; a set of DLC coated surfaces provided on the stationary drum and coming in contact with the rotating shaft; and a thrust support bracket provided with a DLC coated protuberance at one end and attached to a bottom surface of a rim of the stationary drum.
  • FIG. 1 shows a cross sectional view of a ball bearing type head drum assembly of prior art
  • FIG. 2 illustrates a cross sectional view of a sliding bearing type head drum assembly of prior art
  • FIGS. 3A and 3B depict cross sectional views setting forth a head drum assembly in accordance with the present invention
  • FIGS. 4A and 4B provide perspective views illustrating a DLC coated rotating shaft with herring-bone shaped grooves and protrusions, respectively, in accordance with the present invention
  • FIGS. 5A and 5B offer cut away views of a stationary drum with herring-bone shaped grooves and protrusions, respectively, on its DLC coated bearing surfaces, in accordance with the present invention
  • FIG. 6 sets forth a distribution chart demonstrating the load bearing capacity of the air layer between the rotating shaft and bearing surfaces of the stationary drum.
  • FIG. 7 presents a distribution chart explaining the load bearing capacity of the air layer as a function of the depth or height of the herring-bone structures.
  • the head drum assembly 800 for use in a VCR in accordance with the present invention.
  • the head drum assembly 800 comprises a rotating shaft 100 furnished with a DLC coating 110 on its circumferential surface (not shown); a rotary drum 200; a rotor transformer 300; a stator transformer 300'; a stationary drum 400 provided with an annular depression 410 and a pair of bearing surfaces 411 and 421; a ground plate 600; and a motor assembly 700.
  • DLC shall mean a diamond-like carbon, as disclosed in U.S. Pat. No. 5,052,339, entitled “Radio Frequency Plasma Enhanced Chemical Vapor Deposition Process and Reactor", which is incorporated herein by reference.
  • the rotating shaft 100 is divided into an upper portion 101, a lower portion 102, and a motor attachment portion 103.
  • the rotary drum 200 which is provided with a protruding annular portion 210 on its bottom surface, is fitted tightly around the upper portion 101 of the rotating shaft 100.
  • the annular portion 210 encloses a central part 211 of the bottom surface of the rotary drum 200.
  • the inventive head drum assembly 800 it is preferable to leave the parts of the rotating shaft 100 coming in contact with the rotary drum 200 uncoated.
  • the DLC coating functions as an insulator, making it difficult to eliminate a static generated by the rotary drum 200 and the magnetic tape rubbing together. Leaving the parts of the rotating shaft 100 contacting the rotary drum 200 uncoated would facilitate the elimination of static through the use of the ground plate 600 as depicted in FIG. 3A.
  • the stationary drum 400 is fitted around the lower portion 102 of the DLC coated rotating shaft 100.
  • the bearing surfaces 411 and 421 of the stationary drum 400 coming in contact with the rotating shaft 100 are coated with the DLC.
  • the motor assembly 700 which rotates the rotating shaft 100 in relation to the stationary drum 400, is fitted tightly around the motor attachment portion 103 of the rotating shaft 100.
  • an upper thrust plate 500 and a lower thrust plate 500' are installed on the central part 211 of the bottom surface of the rotary drum 200 and the top surface of the axial part of the stationary drum 400, respectively, as a means of bearing axial load.
  • the thrust plates 500 and 500' prevent other surfaces of the rotary drum 200 and the stationary drum 400 from being in direct contact with each other by keeping the rotating shaft 100 and the rotary drum 200 from moving too far down axially.
  • a side 510 of the upper thrust plate 500 and a side 510' of the lower thrust plate 500' that are facing each other are coated with the DLC.
  • the thrust plates 500 and 500' also serve to maintain a set distance between the rotor transformer 300 and the stator transformer 300', which are installed on the protruding annular portion 210 of the rotary drum 200 and a bottom surface of the annular depression 410 of the stationary drum 400, respectively.
  • FIG. 3B illustrates another embodiment of the present invention, wherein a thrust support bracket 750 is employed instead of the thrust plates 500, 500' to prevent the rotary drum 200 from coming in contact with the stationary drum 400.
  • the thrust support bracket 750 is affixed to a bottom surface of a rim (not shown) of the stationary drum 400, and is provided with a protuberance 751 at one end.
  • the protuberance 751 is equipped with a DLC coating 751a, and is in contact with a DLC coated bottom surface of the rotating shaft 100.
  • the thrust support bracket 750 and the DLC coated protuberance 751 prevent the rotating shaft 100 and the rotary drum 200 from moving too far down axially.
  • the DLC is effective enough at reducing friction that only one of the two surfaces that are in contact with each other needs to be coated with the DLC.
  • the rotatability of the rotary drum 200 is also improved due to the fact that the stationary drum 400 is rotatably fitted around the rotating shaft 100 with contact between these two components occurring only through the DLC coated bearing surfaces 411, 421 and the DLC coating 110.
  • the DLC coated surfaces have small frictional coefficients, the rotating shaft 100 and the rotary drum 200 can easily, and with a minimum of friction, rotate in relation to the stationary drum 400.
  • the DLC coating 100 around the rotating shaft 100 may be provided with either a set of herring-bone shaped grooves 110a or a set of herring-bone shaped protrusions 110b, as shown in FIGS. 4A and 4B.
  • a direct contact, and consequently the friction, between the rotating shaft 100 and the stationary drum 400 is reduced.
  • FIGS. 5A and 5B illustrate yet another preferred embodiment of the invention, wherein the DLC coating 110 around the rotating shaft 100 is kept smooth, and the DLC coated bearing surfaces 411 and 421 of the stationary drum 400 are provided with a set of herring-bone shaped grooves 411a and 421a or a set of herring-bone shaped protrusions 411b and 421b.
  • the effect of these herring-bone shaped grooves or protrusions is the same, however, as they still serve to create an air layer between the rotating shaft 100 and the stationary drum 400 that reduces friction.
  • the static friction coefficient between the DLC coated surface and the steel surface is comparable to the static friction coefficient between the lubricated copper surface and the steel surface.
  • the use of the DLC coating 751a on the protuberance 751 prepared at one end of the thrust support bracket 750, or the bottom surface of the rotating shaft 100 makes unnecessary the use of lubricant to reduce friction with the bottom surface of the rotating shaft 100.
  • coating both the protuberance 750 and the rotating shaft 100 with the DLC could improve the rotatability of the rotary drum 200 even more.
  • W is the load capacity
  • Pa is the atmospheric pressure
  • L is the length of the bearing surface
  • D is the diameter of the rotating shaft plus the thickness of the DLC coating on the shaft
  • ⁇ is the air viscosity factor
  • w is the angular velocity of the rotating shaft
  • C is the gap between the bearing surfaces on the stationary drum and the bearing surfaces of the rotating shaft.
  • FIG. 7 presents the relationship between the depth and height of the herring-bone shaped structures, and the load capacity of the air layer. As shown in FIG. 7, the load capacity of the air layer is maximized when the depth or height of the herring-bone shaped grooves or protrusions is in a 5-10 ⁇ m range.
  • the head drum assembly 800 in accordance with the present invention is less likely to wear and tear or malfunction during the operation of the VCR due to defective ball bearings or lubricant contamination of the heads.
  • the present head drum assembly 800 achieves a smooth rotation by utilizing the herring-bone shaped grooves or protrusions in conjunction with the DLC coatings in the appropriate bearing surfaces.
  • the present invention has the added advantage that the formation of the herring-bone shaped grooves or protrusions, either on the rotating shaft 100 or on the bearing surfaces 411, 421, can be accomplished relatively easily through a masking operation during the coating process.
  • herring-bone shaped grooves or protrusions on conventional rotating shafts or stationary drums have to be worked into the shaft or the drum proper, greatly complicating the manufacturing process thereof.
  • the present invention further lowers a manufacturing cost of the head drum assembly by dispensing with the need to carefully measure and apply the lubricant and with the need to provide a thrust support knob made of an expensive material, e.g. a polished ruby.

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  • Engineering & Computer Science (AREA)
  • General Engineering & Computer Science (AREA)
  • Mechanical Engineering (AREA)
  • Physics & Mathematics (AREA)
  • Fluid Mechanics (AREA)
  • Chemical & Material Sciences (AREA)
  • Oil, Petroleum & Natural Gas (AREA)
  • Sliding-Contact Bearings (AREA)
  • Recording Or Reproducing By Magnetic Means (AREA)
US08/573,832 1994-12-27 1995-12-18 Head drum assembly incorporating therein parts coated with diamond-like carbon Expired - Fee Related US5734530A (en)

Applications Claiming Priority (4)

Application Number Priority Date Filing Date Title
KR1994-37247 1994-12-27
KR1019940037247A KR100213272B1 (ko) 1994-12-27 1994-12-27 헤드드럼 조립체
KR1994-36239 1994-12-27
KR2019940036239U KR960024772U (ko) 1994-12-27 1994-12-27 헤드드럼 조립체

Publications (1)

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US5734530A true US5734530A (en) 1998-03-31

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US08/573,832 Expired - Fee Related US5734530A (en) 1994-12-27 1995-12-18 Head drum assembly incorporating therein parts coated with diamond-like carbon

Country Status (5)

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US (1) US5734530A (fr)
EP (1) EP0720155B1 (fr)
JP (1) JPH08235544A (fr)
CN (1) CN1077996C (fr)
DE (1) DE69517785D1 (fr)

Cited By (8)

* Cited by examiner, † Cited by third party
Publication number Priority date Publication date Assignee Title
US6018442A (en) * 1997-04-04 2000-01-25 U.S. Philips Corporation Recording and/or reproducing apparatus having rotary scanning drum supported by a bearing having contacting bearing surfaces which provide electrical grounding
US6487054B1 (en) * 1999-07-22 2002-11-26 Samsung Electronics, Co., Ltd. Ground device of head drum apparatus
US6502991B2 (en) 2001-03-14 2003-01-07 The Timken Company Rotary fluid bearing coatings and coining and processes for manufacturing the same
US20030060839A1 (en) * 2001-08-24 2003-03-27 Nidek Co., Ltd. Corneal surgical apparatus
US6722785B1 (en) * 1999-06-25 2004-04-20 Tdk Corporation Fluid dynamic bearing
US20040190194A1 (en) * 2003-03-28 2004-09-30 Ming-Goei Sheu Data storage device with miniaturized spindle motor
US7718044B2 (en) 2006-09-11 2010-05-18 Seagate Technology Llc Method for controlling shaft coating taper
US20130162083A1 (en) * 2011-12-23 2013-06-27 Samsung Electro-Mechanics Co., Ltd. Spindle motor

Families Citing this family (2)

* Cited by examiner, † Cited by third party
Publication number Priority date Publication date Assignee Title
FR2754627B1 (fr) * 1996-10-11 1998-11-27 Tonnerroise D Electronique Ind Tambour de magnetoscope a palier lisse
DE102008048631A1 (de) * 2008-09-24 2010-03-25 Engineering Center Steyr Gmbh & Co. Kg Asynchronmaschine

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Publication number Priority date Publication date Assignee Title
JPS5989823A (ja) * 1982-11-11 1984-05-24 Matsushita Electric Ind Co Ltd 流体軸受装置
US4875110A (en) * 1985-10-09 1989-10-17 Hitachi Ltd. Rotary head apparatus with motor magnet and yoke surrounding motor stator coil
US4935303A (en) * 1987-10-15 1990-06-19 Canon Kabushiki Kaisha Novel diamond-like carbon film and process for the production thereof
US4972283A (en) * 1987-08-31 1990-11-20 Goldstar Co., Ltd. Rotary head drum for a VCR
US5022339A (en) * 1990-02-21 1991-06-11 Baskin Kermit L Ventilator for attachment to deck hatches
US5142173A (en) * 1989-08-11 1992-08-25 Ebara Corporation Bearing structure
JPH0737233A (ja) * 1993-07-19 1995-02-07 Canon Inc 回転ドラム装置
US5482602A (en) * 1993-11-04 1996-01-09 United Technologies Corporation Broad-beam ion deposition coating methods for depositing diamond-like-carbon coatings on dynamic surfaces
US5486966A (en) * 1993-08-24 1996-01-23 Daewoo Electronics Co., Ltd. Head drum ground system for use in a video cassette recorder
US5539267A (en) * 1994-07-21 1996-07-23 International Business Machines Corporation Microfabricated rotary motion wobble motor and disk drive incorporating it

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Publication number Priority date Publication date Assignee Title
US5052339A (en) 1990-10-16 1991-10-01 Air Products And Chemicals, Inc. Radio frequency plasma enhanced chemical vapor deposition process and reactor

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Publication number Priority date Publication date Assignee Title
JPS5989823A (ja) * 1982-11-11 1984-05-24 Matsushita Electric Ind Co Ltd 流体軸受装置
US4875110A (en) * 1985-10-09 1989-10-17 Hitachi Ltd. Rotary head apparatus with motor magnet and yoke surrounding motor stator coil
US4972283A (en) * 1987-08-31 1990-11-20 Goldstar Co., Ltd. Rotary head drum for a VCR
US4935303A (en) * 1987-10-15 1990-06-19 Canon Kabushiki Kaisha Novel diamond-like carbon film and process for the production thereof
US5142173A (en) * 1989-08-11 1992-08-25 Ebara Corporation Bearing structure
US5022339A (en) * 1990-02-21 1991-06-11 Baskin Kermit L Ventilator for attachment to deck hatches
JPH0737233A (ja) * 1993-07-19 1995-02-07 Canon Inc 回転ドラム装置
US5486966A (en) * 1993-08-24 1996-01-23 Daewoo Electronics Co., Ltd. Head drum ground system for use in a video cassette recorder
US5482602A (en) * 1993-11-04 1996-01-09 United Technologies Corporation Broad-beam ion deposition coating methods for depositing diamond-like-carbon coatings on dynamic surfaces
US5539267A (en) * 1994-07-21 1996-07-23 International Business Machines Corporation Microfabricated rotary motion wobble motor and disk drive incorporating it

Non-Patent Citations (4)

* Cited by examiner, † Cited by third party
Title
English Abstract of Japanese document 59 089823 (May/1984). *
English Abstract of Japanese document 59-089823 (May/1984).
English Abstract of Japanese document 7 037233 (Feb./1995). *
English Abstract of Japanese document 7-037233 (Feb./1995).

Cited By (13)

* Cited by examiner, † Cited by third party
Publication number Priority date Publication date Assignee Title
US6018442A (en) * 1997-04-04 2000-01-25 U.S. Philips Corporation Recording and/or reproducing apparatus having rotary scanning drum supported by a bearing having contacting bearing surfaces which provide electrical grounding
US6722785B1 (en) * 1999-06-25 2004-04-20 Tdk Corporation Fluid dynamic bearing
US6487054B1 (en) * 1999-07-22 2002-11-26 Samsung Electronics, Co., Ltd. Ground device of head drum apparatus
US6502991B2 (en) 2001-03-14 2003-01-07 The Timken Company Rotary fluid bearing coatings and coining and processes for manufacturing the same
US20030060839A1 (en) * 2001-08-24 2003-03-27 Nidek Co., Ltd. Corneal surgical apparatus
US20050225896A1 (en) * 2003-03-28 2005-10-13 Esgw Holdings Limited Trustnet (British Virgin Islands) Limited Data storage device with a low profile spindle motor
US20040190194A1 (en) * 2003-03-28 2004-09-30 Ming-Goei Sheu Data storage device with miniaturized spindle motor
US6961210B2 (en) * 2003-03-28 2005-11-01 Esgw Holdings Limited Data storage device with a low profile spindle motor
US7154704B2 (en) * 2003-03-28 2006-12-26 Esgw Holdings Limited Data storage device with a low profile spindle motor having hub and drive member arranged on opposite sides of a baseplate
US7718044B2 (en) 2006-09-11 2010-05-18 Seagate Technology Llc Method for controlling shaft coating taper
US20100184521A1 (en) * 2006-09-11 2010-07-22 Seagate Technology Llc Method for controlling shaft coating taper
US8622844B2 (en) 2006-09-11 2014-01-07 Seagate Technology Llc Tapered shaft coating
US20130162083A1 (en) * 2011-12-23 2013-06-27 Samsung Electro-Mechanics Co., Ltd. Spindle motor

Also Published As

Publication number Publication date
DE69517785D1 (de) 2000-08-10
CN1077996C (zh) 2002-01-16
EP0720155A1 (fr) 1996-07-03
CN1135629A (zh) 1996-11-13
JPH08235544A (ja) 1996-09-13
EP0720155B1 (fr) 2000-07-05

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